CN104204612A - Multi-speed gearbox - Google Patents
Multi-speed gearbox Download PDFInfo
- Publication number
- CN104204612A CN104204612A CN201380017986.7A CN201380017986A CN104204612A CN 104204612 A CN104204612 A CN 104204612A CN 201380017986 A CN201380017986 A CN 201380017986A CN 104204612 A CN104204612 A CN 104204612A
- Authority
- CN
- China
- Prior art keywords
- gear
- clutch
- break
- gear train
- train
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates a four-speed multi-speed gearbox in which a planet carrier (12) of a first planetary gear set (1) is connected to a ring gear (43) of a fourth planetary gear set (4), a ring gear (13) of the first planetary gear set (4) and a planet carrier (22) of a second planetary gear set (2) can be coupled by means of a first brake (51) to the housing (72) or by means of a first clutch (61) to the drive shaft (70), a sun gear (11) of the first planetary gear set (1) and a sun gear (21) of the second planetary gear set (2) can be coupled to the housing (72) by means of a second brake (52), a sun gear (31) of a third planetary gear set (3) and a sun gear (41) of the fourth planetary gear set (4) can be coupled to the housing (72) by means of a third brake (53), the drive shaft (70) can be coupled to a ring gear (23) of the second planetary gear set (2); by means of a second clutch (62), a ring gear (33) of the third planetary gear set (3) and a planet carrier (42) of the fourth planetary gear set (4) can be coupled to the drive shaft (70) by means of a third clutch (63) and the output shaft (71) is connected to a planet carrier (32) of the third planetary gear set (3).
Description
Technical field
The present invention relates to a kind of multiple-speed gear-box of planet structural form, especially for Motor Vehicle.
Background technique
This class multiple-speed gear-box is preferably as the automatic transmission of Motor Vehicle, and wherein, the useful horsepower that defines the planetary gear set inside in corresponding gear level by handling targetedly shifting element flows.At this, in automatic transmission, planetary gear set conventionally also with bear initiating element slippage effect and that be furnished with alternatively lock-up clutch and be connected, be for example connected with fluid torque converter or hydraulic couplers.
Known a kind of multiple-speed gear-box of planet structural form in DE 10 2,008 000 428 A1, wherein, in housing, arranged four planetary set, and eight rotating axles altogether, one of them is live axle and another driven shaft that is multiple-speed gear-box of multiple-speed gear-box.In addition, in the region of these axles, be provided with at least six shifting elements, by operating targetedly these shifting elements, the power stream in these four planetary set changed, and therefore can limit the different velocity ratio between live axle and driven shaft.Generally speaking, can switch thus nine forward gears and one reverses gear.
Summary of the invention
Task of the present invention is, a kind of alternative multiple-speed gear-box is provided, and it preferably has improved efficiency and has enough large and enough uniform velocity ratio sequences that distributes.
Task of the present invention is solved according to multiple-speed gear-box claimed in claim 1 by a kind of.Particularly by a kind of, comprise that the multiple-speed gear-box of at least four planetary gear set, housing, live axle and driven shaft is solved, wherein
The planet carrier of the-the first planetary gear set is connected enduringly with the gear ring of fourth planet gear train,
The gear ring of the-the first planetary gear set can connect with housing by the first break with the planet carrier of the second planetary gear set, or can connect with live axle by first clutch,
The sun gear of the sun gear of the-the first planetary gear set and the second planetary gear set can connect with housing by second brake,
The sun gear of the sun gear of-third planet gear train and fourth planet gear train can connect with housing by the 3rd break,
-live axle can connect with the gear ring of the second planetary gear set by second clutch,
The planet carrier of the gear ring of-third planet gear train and fourth planet gear train can connect with live axle by the 3rd clutch, and
-driven shaft is connected enduringly with the planet carrier of third planet gear train.
Planetary gear set is particularly understood as a kind of like this gear train, and this gear train comprises at least one sun gear (one or more planetary pinion and the engagement of this sun gear); Also comprise the planet carrier of determining planetary axis; And comprise gear ring, planetary pinion and the engagement of this gear ring.Preferably, gear ring has internal tooth portion and sun gear has outer toothed portion.
Advantage of the present invention can be from outside, can contact at an easy rate the shifting element of multiple-speed gear-box, namely the break of transmission side and clutch.Therefore, can near shifting element, arrange actuator, for example motor, hydrovalve, oil hydraulic pump and similar device, can reduce machinery and/or hydraulic pressure loss thus, and can reduce for operating the needed energy of shifting element.And (open or closed) needed energy also can reduce for shifting element correspondingly being remained under its current running state, for example this is because also reduced pressure loss by short pipeline.This also can realize and shifting element being arranged on housing and therefore disposed thereon in anti-relative rotation at least partly, thus can be fully or partly save the Sealing for the pipeline of static pipeline and rotation is coupled together.
Layout on this space of the shifting element that can touch at an easy rate also simplified by for example can be fairly simple drive as required break control, the operation of electromechanical formula or electric hydraulic type and clutch replaces lamella clutch or chip break common, hydraulic type operation.The shifting element that can touch is at an easy rate those breaks that axle is connected in anti-relative rotation with housing on the one hand, but can be also on the axle of outer placement of multiple-speed gear-box, the preferred shifting element on live axle or driven shaft, for operate needed hydraulic fluid can be fairly simple flow to these axles.
Except this characteristic, multiple-speed gear-box also has good meshing efficiency, only very little member load, and particularly little planetary gear set moment and the moment of shifting element, low absolute rotating speed and relative rotation speed and/or a small amount of structure expend.The latter make to realize only have very little weight and cheaply multiple-speed gear-box become possibility.Finally, the level that can well use that multiple-speed gear-box also makes good velocity ratio sequence namely keep off becomes possibility.
In general, multiple-speed gear-box preferred embodiment comprise four planetary gear set, three clutches and three breaks, and there is no fixing housing joint part.
By operating respectively two shifting elements (break and/or clutch), can switch nine forward gears and one and reverse gear, wherein, for the 4th gear provides three other alternative drive ranges.
The clutch of fluid torque converter, hydraulic type, additional starting clutch, integrated starting clutch or starting break and/or additional motor can be used as initiating element.
On each axle, can arrange in principle motor or other power source/power source.In addition on each axle, can arrange in principle towards housing or towards the freewheel of another axle.
Preferably, multiple-speed gear-box is embodied as standard drive unit, but also can consider the laterally make of preposition (Front-Quer).
All shifting elements can both rub, and sealed (Reibschl ü ssig) or shape are sealed works (Formschl ü ssig).Yet preferably, the 3rd break may be embodied as the sealed shifting element of shape, is particularly embodied as jaw clutch, this can obviously improve efficiency and therefore advantageously obviously reduce and consume.
At this, it has been found that, when being switched to nine gears from a gear, only must operate the 3rd break once.Therefore, this shifting element is particularly suitable for being embodied as jaw clutch.Further find, in this shifting element, owing to less operating, so the higher advantage of efficiency makes the more difficult shortcoming of operation inessential.Particularly find, when higher gear, can carry out the operation to this shifting element, thus can be so that the speed discrepancy of axle be very little, and be therefore conducive to the current operation to jaw clutch.
As long as each gear train and shifting element can couple together, can freely select their geometric position, particularly their sequence.Therefore, each element can at random be moved on their position.
By dependent claims and in description taken in conjunction with the accompanying drawings book, draw other favourable flexible program of multiple-speed gear-box.These flexible programs all have the characteristic as main system in function, particularly similarly efficiency, similarly classification etc.
Accompanying drawing explanation
In order to understand better the present invention, by the following drawings, it is carried out to more detailed description.
View with height simplified schematic illustrates respectively:
Fig. 1 illustrates first exemplary variation scheme schematically showing according to multiple-speed gear-box of the present invention; And
Fig. 2 illustrates a form, and it shows the closed shifting element in each gear level for the speed changer flexible program shown in Fig. 1.
Embodiment
The position description of selecting in specification, such as above, below, side etc., be with regard to Direct function description and shown in accompanying drawing with regard to, and can correspondingly be applicable to new position when change in location.In addition, single feature or the Feature Combination itself from shown and described embodiment also can represent independently, creative or according to solution of the present invention.
Fig. 1 illustrates multiple-speed gear-box, and it comprises four planetary gear set 1,2,3,4; Live axle 70; Driven shaft 71, six other rotating axles 73,74,75,76,77,78; Six shifting elements 51,52,53,61,62,63 (wherein, being 51,52,53 and three clutches 61,62,63 of three breaks).Four planetary gear set 1,2,3,4 are one after the other arranged with the order of the first planetary gear set 1, the second planetary gear set 2, third planet gear train 3, fourth planet gear train 4.The first planetary gear set 1, the second planetary gear set 2, third planet gear train 3 and fourth planet gear train 4 are configured to negative planetary gear set.These planetary gear set 1,2,3,4 are jointly surrounded by housing 72.Pressing in the flexible program shown in Fig. 1 of multiple-speed gear-box,
The planet carrier 12 of the-the first planetary gear set 1 is connected enduringly with the gear ring 43 of fourth planet gear train 4,
The gear ring 13 of the-the first planetary gear set 1 and the planet carrier 22 of the second planetary gear set 2 can connect with housing 72 by the first break 51, or can connect with live axle 70 by first clutch 61,
The sun gear 11 of the-the first planetary gear set 1 and the sun gear 21 of the second planetary gear set 2 can connect with housing 72 by second brake 52,
The sun gear 31 of-third planet gear train 3 and the sun gear 41 of fourth planet gear train 4 can connect with housing 72 by the 3rd break 53,
-live axle 70 can connect by second clutch 62 with the gear ring 23 of the second planetary gear set 2,
The gear ring 33 of-third planet gear train 3 and the planet carrier 42 of fourth planet gear train 4 can connect with live axle 70 by the 3rd clutch 63,
-driven shaft 71 is connected enduringly with the planet carrier 32 of third planet gear train 3.
In the multiple-speed gear-box shown in Fig. 1, can switch with lower block:
By closed second brake 52, closed the 3rd break 53 and closed second clutch 62, can realize the first gear.
By closed second brake 52, closed the 3rd break 53 and closed first clutch 61, can realize the second gear.
By the 3rd break 53 of closure, closed first clutch 61 and closed second clutch 62, can realize the 3rd gear.
The 3rd break 53 by closure, closed first clutch 61 and closed the 3rd clutch 63 or
The 3rd break 53 by closure, closed second clutch 62 and closed the 3rd clutch 63 or
By closed second brake 52, closed the 3rd break 53 and closed the 3rd clutch 63 or
By the first break 51 of closure, closed the 3rd break 53 and the 3rd closed clutch 63, can realize the 4th gear.
By closed first clutch 61, closed second clutch 62 and the 3rd closed clutch 63, can realize the 5th gear.
By closed second brake 52, closed first clutch 61 and the 3rd closed clutch 63, can realize the 6th gear.
By closed second brake 52, closed second clutch 62 and the 3rd closed clutch 63, can realize the 7th gear.
By the first break 51 of closure, closed second brake 52 and the 3rd closed clutch 63, can realize the 8th gear.
By the first break 51 of closure, closed second clutch 62 and the 3rd closed clutch 63, can realize the 9th gear.
The first break 51 by closure is, the 3rd closed break 53 and closed second clutch 62 can be realized reverses gear.
At this, corresponding NM shifting element is all opened.
This wherein, also shows the velocity ratio of each gear level also shown in the form of Fig. 2.
Preferably, in shown multiple-speed gear-box, all gear trains 1,2,3,4 are all embodied as negative gear train.
In a kind of favourable flexible program:
The velocity ratio of-the first gear train 1 between sun gear 11 and gear ring 13 is-2.303, and/or
The velocity ratio of-the second gear train 2 between sun gear 21 and gear ring 23 is-1.613, and/or
The velocity ratio of-the 3rd gear train 3 between sun gear 31 and gear ring 33 is-2.899, and/or
The velocity ratio of-the 4th gear train 4 between sun gear 41 and gear ring 43 is-3.074.
Generally speaking, as gear train 1, 2, 3, 4 with planet carrier 12, 22, 32, the first connection of mentioning of 42/connect and this gear train 1, 2, 3, 4 with gear ring 13, 23, 33, the second replacement that connects/connect of mentioning of 43, can implement this gear train 1, 2, 3, 4 with described gear ring 13, 23, 33, the first connection of mentioning of 43/connect and this gear train 1, 2, 3, 4 with described planet carrier 12, 22, 32, the second connect/connection of 42, wherein, gear train 1, 2, 3, 4 replace being embodied as negative gear train is embodied as commutating tooth wheels, or replace being embodied as commutating tooth wheels and be embodied as negative gear train.In other words, gear train 1,2,3,4 and planet carrier 12,22,32,42 and with being connected/connecting and be replaced of gear ring 13,23,33,43, and the sun gear 11,21,31,41 of this gear train 1,2,3,4 and the reversion of the sense of rotation between gear ring 13,23,33,43.In the design proposal of multiple-speed gear-box, extra care, when the switchable velocity ratio between drive unit 70 and driven device 71 should remain unchanged, the numerical value of the intrinsic velocity ratio of this gear train will increase or reduce by 1.Described flexible program by gear train 1,2,3,4 just can change the connection/connection between each transmission component, and does not change the characteristic of this speed changer simultaneously.Therefore provide many structural design proposals, they can make the realization of speed changer be simplified under individual cases.At this, the replacing of connection/connection of mentioning is not limited to a gear train 1,2,3,4, but also can be applied on a plurality of gear trains 1,2,3,4 simultaneously.
These embodiments show the possible enforcement flexible program according to multiple-speed gear-box of the present invention, wherein, what at this, notice is, the present invention is not limited to these the enforcement flexible programs that illustrate especially according to multiple-speed gear-box of the present invention, but can be also exactly that each implements flexible program various combination to each other, and the instruction based on technological means, by concrete invention, within this flexible program possibility belongs to those skilled in the art of the present technique's limit of power.The scheme particularly drawing in combinatorics and claim 1, but obviously do not illustrate in the accompanying drawings is also included in protection domain.In addition, all thinkable, can be included in protection domain by combining the enforcement flexible program that each details of shown and described enforcement flexible program draws.
What finally for regulation, will indicate is, in order to understand better the structural scheme of described multiple-speed gear-box, therefore schematically shown in the drawings this multiple-speed gear-box, and in reality, may comprise than more, the member still less illustrating or the member that comprises other.Generally speaking, design proposal concrete, structurally is all in those skilled in the art's limit of power.
From specification, can know based on independently, the task of creative solution.
Reference numerals list
1 first transmission gear group
2 second transmission gear groups
3 the 3rd transmission gear groups
4 the 4th transmission gear groups
The sun gear of 11 first transmission gear groups
The planet carrier of 12 first transmission gear groups
The gear ring of 13 first transmission gear groups
The sun gear of 21 second transmission gear groups
The planet carrier of 22 second transmission gear groups
The gear ring of 23 second transmission gear groups
The sun gear of 31 the 3rd transmission gear groups
The planet carrier of 32 the 3rd transmission gear groups
The gear ring of 33 the 3rd transmission gear groups
The sun gear of 41 the 4th transmission gear groups
The planet carrier of 42 the 4th transmission gear groups
The gear ring of 43 the 4th transmission gear groups
51 first breaks
52 second brakes
53 the 3rd breaks
61 first clutches
62 second clutches
63 the 3rd clutches
70 drive units
71 driven devices
72 housings
73,74,75,76,77,78 axles
Claims (6)
1. a multiple-speed gear-box,
Described multiple-speed gear-box comprises at least four planetary gear set (1,2,3,4), housing (72), live axle (70) and driven shaft (71), wherein
The planet carrier (12) of the-the first planetary gear set (1) is connected enduringly with the gear ring (43) of fourth planet gear train (4),
The gear ring (13) of-described the first planetary gear set (1) and the planet carrier (22) of the second planetary gear set (2) can connect with described housing (72) by the first break (51), or can pass through first clutch (61) connects with described live axle (70)
The sun gear (11) of-described the first planetary gear set (1) and the sun gear (21) of described the second planetary gear set (2) can pass through second brake (52) and connect with described housing (72),
The sun gear (31) of-third planet gear train (3) and the sun gear (41) of described fourth planet gear train (4) can connect with described housing (72) by the 3rd break (53),
-described live axle (70) can pass through second clutch (62) and connect with the gear ring (23) of described the second planetary gear set (2),
The gear ring (33) of-described third planet gear train (3) and the planet carrier (42) of described fourth planet gear train (4) can connect with described live axle (70) by the 3rd clutch (63), and
-described driven shaft (71) is connected enduringly with the planet carrier (32) of described third planet gear train (3).
2. according to multiple-speed gear-box claimed in claim 1, it is characterized in that, the element that can provide by closure is switched to as lower block:
-by second brake (52), the 3rd break (53) and second clutch (62), be switched to a gear;
-by second brake (52), the 3rd break (53) and first clutch (61), be switched to two gears;
-by the 3rd break (53), first clutch (61) and second clutch (62), be switched to three gears;
-by the 3rd break (53), first clutch (61) and the 3rd clutch (63) or
-by the 3rd break (53), second clutch (62) and the 3rd clutch (63) or
-by second brake (52), the 3rd break (53) and the 3rd clutch (63) or
-by the first break (51), the 3rd break (53) and the 3rd clutch (63), be switched to four gears;
-by first clutch (61), second clutch (62) and the 3rd clutch (63), be switched to five gears;
-by second brake (52), first clutch (61) and the 3rd clutch (63), be switched to six gears;
-by second brake (52), second clutch (62) and the 3rd clutch (63), be switched to seven gears;
-by the first break (51), second brake (52) and the 3rd clutch (63), be switched to eight gears;
-by the first break (51), second clutch (62) and the 3rd clutch (63), be switched to nine gears; And
-by the first break (51), the 3rd break (53) and second clutch (62), be switched to and reverse gear,
Wherein, each NM element is operated or perhaps open.
3. according to the multiple-speed gear-box described in any one in claim 1 or 2, it is characterized in that, all gear trains (1,2,3,4) are all embodied as negative gear train.
4. according to multiple-speed gear-box claimed in claim 3, it is characterized in that,
The velocity ratio of-described the first gear train (1) between sun gear (11) and gear ring (12) is-2.303, and/or
The velocity ratio of-described the second gear train (2) between sun gear (21) and gear ring (22) is-1.613, and/or
The velocity ratio of-described the 3rd gear train (3) between sun gear (31) and gear ring (32) is-2.899, and/or
The velocity ratio of-described the 4th gear train (4) between sun gear (41) and gear ring (42) is-3.074.
5. according to the multiple-speed gear-box described in any one in claim 1 to 4, it is characterized in that, as gear train (1, 2, 3, 4) with planet carrier (12, 22, 32, 42) the first connection of mentioning/connect and this gear train (1, 2, 3, 4) with gear ring (13, 23, 33, 43) the second replacement that connects/connect of mentioning, implemented this gear train (1, 2, 3, 4) with described gear ring (13, 23, 33, 43) the first connection/connect and this gear train (1, 2, 3, 4) with described planet carrier (12, 22, 32, 42) the second connect/connection, wherein, this gear train (1, 2, 3, 4) replace being embodied as negative gear train and be embodied as commutating tooth wheels, or replace being embodied as commutating tooth wheels and be embodied as negative gear train.
6. according to the multiple-speed gear-box described in any one in claim 1 to 5, it is characterized in that, described the first break (53) is embodied as jaw clutch.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201210207043 DE102012207043A1 (en) | 2012-04-27 | 2012-04-27 | Multi-speed transmission |
| DE102012207043.5 | 2012-04-27 | ||
| PCT/EP2013/055060 WO2013159991A1 (en) | 2012-04-27 | 2013-03-13 | Multi-speed gearbox |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104204612A true CN104204612A (en) | 2014-12-10 |
| CN104204612B CN104204612B (en) | 2016-09-21 |
Family
ID=47997390
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380017986.7A Expired - Fee Related CN104204612B (en) | 2012-04-27 | 2013-03-13 | Multiple-speed gear-box |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US9371891B2 (en) |
| EP (1) | EP2841812A1 (en) |
| CN (1) | CN104204612B (en) |
| DE (1) | DE102012207043A1 (en) |
| WO (1) | WO2013159991A1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114562A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission with planet gear structure mode |
| CN105114561A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Automatic nine-gear transmission |
| CN105114560A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission achieved in mode of planetary gear structure |
| CN105697684A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | planetary gear train of automatic transmission for vehicles |
| CN105697685A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN105697683A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicles |
| CN107202120A (en) * | 2016-03-17 | 2017-09-26 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN114001132A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012206809B4 (en) * | 2012-04-25 | 2021-03-11 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102012218687B4 (en) * | 2012-10-15 | 2021-09-30 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US10584771B2 (en) | 2015-09-09 | 2020-03-10 | Volvo Construction Equipment Ab | Transmission arrangement for a vehicle |
| EP3347620B1 (en) | 2015-09-09 | 2020-10-28 | Volvo Construction Equipment AB | A transmission arrangement for a vehicle |
| EP3347621B1 (en) | 2015-09-09 | 2020-11-04 | Volvo Construction Equipment AB | A transmission arrangement for a vehicle |
| KR20180003158A (en) | 2016-06-30 | 2018-01-09 | 현대자동차주식회사 | Planetary gear train of automatic transmission for vehicles |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1592824A (en) * | 2001-03-30 | 2005-03-09 | 腓特烈斯港齿轮工厂股份公司 | Multi-gear speed variator |
| JP2005083479A (en) * | 2003-09-09 | 2005-03-31 | Kyowa Metal Work Co Ltd | Multistage shift planetary gear train |
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| CN101970902A (en) * | 2008-02-28 | 2011-02-09 | Zf腓德烈斯哈芬股份公司 | Multi-stage gearbox |
| DE102009028670A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Planetary type multi-ratio transmission i.e. automatic transmission for passenger car, has shaft connected with sun wheels of two planetary sets and coupled to housing by brake, and driven shaft connected with bar of one of planetary sets |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006349153A (en) | 2005-06-14 | 2006-12-28 | Hiroki Kawana | Gear train for nine-speed automatic transmission |
| US7695398B2 (en) | 2007-07-09 | 2010-04-13 | Gm Global Technology Operations, Inc. | 9-speed transmission |
| DE102008038210B4 (en) | 2007-08-24 | 2017-06-22 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Multi-speed transmission |
| US7946948B2 (en) | 2008-01-31 | 2011-05-24 | GM Global Technology Operations LLC | 9-speed transmission |
| DE102008000429A1 (en) | 2008-02-28 | 2009-09-03 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102008041209B4 (en) | 2008-08-13 | 2018-08-23 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102008041196B4 (en) | 2008-08-13 | 2017-11-30 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102008041200B4 (en) | 2008-08-13 | 2018-06-07 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102009047279A1 (en) | 2009-11-30 | 2011-06-01 | Zf Friedrichshafen Ag | Multi-speed transmission in planetary design, particularly automatic transmission for motor vehicle, has drive shaft, output shaft, four planetary gear sets arranged in housing, eight rotatable shafts and six switching elements |
-
2012
- 2012-04-27 DE DE201210207043 patent/DE102012207043A1/en not_active Ceased
-
2013
- 2013-03-13 EP EP13711862.6A patent/EP2841812A1/en not_active Withdrawn
- 2013-03-13 US US14/396,082 patent/US9371891B2/en not_active Expired - Fee Related
- 2013-03-13 WO PCT/EP2013/055060 patent/WO2013159991A1/en active Application Filing
- 2013-03-13 CN CN201380017986.7A patent/CN104204612B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1592824A (en) * | 2001-03-30 | 2005-03-09 | 腓特烈斯港齿轮工厂股份公司 | Multi-gear speed variator |
| JP2005083479A (en) * | 2003-09-09 | 2005-03-31 | Kyowa Metal Work Co Ltd | Multistage shift planetary gear train |
| CN101970902A (en) * | 2008-02-28 | 2011-02-09 | Zf腓德烈斯哈芬股份公司 | Multi-stage gearbox |
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| DE102009028670A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Planetary type multi-ratio transmission i.e. automatic transmission for passenger car, has shaft connected with sun wheels of two planetary sets and coupled to housing by brake, and driven shaft connected with bar of one of planetary sets |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697684A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | planetary gear train of automatic transmission for vehicles |
| CN105697685A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN105697683A (en) * | 2014-12-11 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicles |
| CN105697684B (en) * | 2014-12-11 | 2019-05-31 | 现代自动车株式会社 | The planetary gear train of automatic transmission for vehicle |
| CN105697683B (en) * | 2014-12-11 | 2019-07-05 | 现代自动车株式会社 | The planetary gear train of automatic transmission for vehicle |
| CN105697685B (en) * | 2014-12-11 | 2019-08-09 | 现代自动车株式会社 | The planetary gear train of automatic transmission for vehicle |
| CN105114562A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission with planet gear structure mode |
| CN105114561A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Automatic nine-gear transmission |
| CN105114560A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission achieved in mode of planetary gear structure |
| CN107202120A (en) * | 2016-03-17 | 2017-09-26 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN114001132A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104204612B (en) | 2016-09-21 |
| US20150126325A1 (en) | 2015-05-07 |
| WO2013159991A1 (en) | 2013-10-31 |
| US9371891B2 (en) | 2016-06-21 |
| DE102012207043A1 (en) | 2013-10-31 |
| EP2841812A1 (en) | 2015-03-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104204612A (en) | Multi-speed gearbox | |
| CN104204611A (en) | Multi-speed gearbox | |
| CN104271986A (en) | Multi-speed gearbox | |
| CN104136808B (en) | Multistage transmission | |
| CN104204610B (en) | Multiple-speed gear-box | |
| CN104114904A (en) | Multi-stage planetary vehicle transmission | |
| CN102498318B (en) | Multi-ratio transmission | |
| CN102472371B (en) | Multi-ratio transmission | |
| CN104334921B (en) | Multiple-speed gear-box | |
| CN104136807A (en) | Multi-stage planetary vehicle transmission | |
| US7517297B2 (en) | Multistage transmission | |
| CN104254713B (en) | Multiple-speed gear-box | |
| CN102954162B (en) | There is the multi-shifting speed variator of engine starting/stopping enabler | |
| CN105074276A (en) | Multi-stage planetary gear mechanism | |
| CN105051416A (en) | Transmission for a motor vehicle | |
| CN104220778B (en) | Multiple-speed gear-box | |
| CN104145135B (en) | Multiple-speed gear-box | |
| CN104254710A (en) | Multi-speed gearbox | |
| CN104246295B (en) | Multiple-speed gear-box | |
| CN104271984B (en) | Multiple-speed gear-box | |
| CN104246294A (en) | Multi-speed gearbox | |
| CN104718399A (en) | Multi-stage transmission | |
| CN104094020A (en) | Multi-ratio transmission | |
| CN204459021U (en) | Multiple-speed gear-box | |
| CN104081088A (en) | Multi-ratio transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160921 Termination date: 20210313 |